Machine for generating fine pitch and other gears



M h 27, 1945. E, w WLLER 2,372,596

MACHINE FOR GENERATING FINE PITCH AND OTHER GEARS Filed July 14, 1959 15 Sheets-Sheet l March 27, 1945. w MlLLER 2,372,596

7 MACHINE FOR GENERATING FINE PITCH AND OTHER GEARS Filed July 14, 1959 15 Sheets-Sheet 2 22Z zz7 Z26 Zdzvard WM'ZZer, r Z06 wk; ,5 Q

March 27, 1945.

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MACHINE FOR GENERATING FINE PITCH AND OTHER GEARS Filed July 14/1939 15 Sheets-Sheet 5 1320932303 Z'dwawd WM'ZZez- March 27, 1945. 4 w MILLER 2,372,596

MACHINE FOR GENERATING FINE PITCH AND OTHER GEARS Filed July ,14, 1939 15 Sheeis-Sheet Mam-ch 27, 1945. E. w. 'MlLLER -MACHINE FOR GENERATING, FINE PITCH AND OTHER GEARS Filed J uly 14, 1959 15 Sheets-Sheet 7 w gz,

March 27, 1945. 2,372,596

- MACHINE FQRGENERATING FINE FITCH AND OTHER GEARS E. w. MILLER Filed July 14, 1939 15 Sheets-Sheet 8 \k //V v 1 w 1 I F /A// wfle m P a 2 u w 5 I 7 a a W 7 7 9 W 0 9w 8 Z 2 a a 1 9E ......|1 w g g a w a 9 I 6 F m 6 5 6 g m 6 a M March 27, 1945.

E. w. MILLER v 7 6 MACHINE FOR GENERATING FINE PITCH AND OTHER GEARS Filed July 14, 1939 15 Sheets-Sheet 9 1.? Foam 13 d W March 27, 1945. E. w. M ILLER 2,372,596

MACHINE FOR GENERATING FINE PITCH AND OTHER GEARS I Filed July 14, 1939 1'5 Sheets-Sheet 10 March 27, 1945. "w. M 2,372,596

r MACHINE FOR GENERATING FINE PITCH AND OTHER GEARS Filed July 14, 1939 15 Sheets-Sheet 11 March 2-7, 1945. E. W.M ILLER 2,372,596

MA CHINE FOR GENERATING FINE .P ITCH AND OTHER GEARS Filed July 14, 1959 15 Sheets-Sheet 12 March 27, 1945. E. w. MILLER MACHINE FOR GENERATING FINE PITCH AND OTHER GEARS Fil'ed July 14, 1939 15 Sheets-Sheet 15 MACHINE FOR GENERATING FINE PITCX-j AND OTHER GEARS Filed July 14; 1959 15 Sheets-Sheet l4 1520922303 v l'dzvaz d enema Mar. 21, 1945 MACHINE FOR GENERATING FINE PITCH AND OTHER GEES Edward W. Miller, Springfield, Vt., asslgnor to The Fellows Gear Shape: Company, Springfield, Vt., a corporation of Vermont Application July 14, 1939, Serial No. 284,416 42 claiins. (Cl. 90--8') The present invention is principally concerned with machines for cutting by the molding generating process gears of very fine pitches. However, many of the principles of the invention are applicable to the cutting of coarse pitch gears,

' cams and other articles of similar or analogous character, also, wherefore the protection which I seek is not to be construed as limited to the production of line pitch gears only. But the main object I have sought and accomplished is to en able gears of extremely fine pitches to be generated and out within unusually narrow limits of accuracy. Gears of the character referred to are the plnions and gears of watches, and those which are used in measuring instruments-motion picture cameras and projectors, and other mechanisms employing small gears and in which the greatest possible accuracy is highly desirable. Such gears have not been inadewith the desired accuracy of tooth forms and dimensions,

heretofore because of the limitations oi. the machines and equipment available up to this time for cutting them.

In accomplishing the object set forth I have devised a cutter in the form of a rack with teeth equal to, or exceeding in number, the number of teeth to be out in a given workpiece, or a multiple of that number; such cutter having cutting edges at one end of its teeth and the sides of the teeth being relieved for cutting clearance. with such cutter I have combined means for reciprocating it in the direction of the length of its teeth (which is transverse to the length of the cutter as a whole), for performing the cutting action, and means for giving it a progressive gerieratlng travel lengthwise of the rack as a whole helix angles. sun another object otthe invention is to shorten the time consumed in changing the work, which 1 have accomplished by providing a magazine adapted to hold a plurality of blank work pieces, combined with mechanism for effecting an automatic delivery of blanks from the- .magazine to the cutting position on the completion of each work piece.

. Theseand other features of the inventions are fully described and explained in the followin specification in connection with drawings which illustrate some of the forms in which the primalples of the invention may be embodied,

In the drawings referred to, Fig. l is a front-elevation, Fig. 2 a rear elevation, Fig. 3 a plan View, and Fig. 4 a side elevation as seen from the right of Figs. 1 and 3, of a complete machine containing one embodiment of the invention;

Fig. 5 is a vertical section of the machine taken on line 5-5 of Figs. 1, 3 and '7 and shown on a larger scale;

Fig. 6 is a vertical cross section and partial elevation of the machine as taken on line 6-3 of Figs. 3, t and 5;

.Fig. 6c is a fragmentary elevation of the cutter head of this machine showing the adjustment :lor

while the work is rotated at equal linear pitch line velocity. I have further provided novel cutting helical gears of approi'zimately 4&5" .ielin angle;

Fig. '7 is a vertical cross section taken on line ll of Fig. 5; r

Fig. 813s a sectional plan view taken on line t t;

Fig. 14 is a detail horizontal section. taken on line Ill-64 of Fig. 13 and drawn on a larger scale; Fig. 15 lsa horizontal section of one form of the magazine for the blank work pieces taken 0 line 115-45 of Figs. 13 and 16;

Flg. 16 is a front elevation of the magazln shown in Fig. 15;

Fig. 17 is a cross section of the magazine and accessory parts taken on line il -W of Figs. 15 and 16; V

Mg, 18 is a plan view of a form of the machine containing other embodiments of certain features of the invention;

Fig. 19 is a vertical section on line l9--l 9 of Fig. 18; Y t

Figs. 20 and 21 are horizontal sections on lines 20-20 and 2i--2l respectively cf Fig.119; v

Fig. 22 is a vertical section on line 22--22 o! Fi .1

Fig. 23 is a detail horizontal section on line "-23 of Fig. 22; 1 Y

Figs. 24 and 35 are fragmentary views showing different forms of work clamping means adapted to be substituted for the work clamping means shown in certain of the preceding figures;

Fig. 26 is an enlarged detail of the work adapter shown in Fig. 25; r J Fig. 27 is a side elevation ofa form of the ma.-. chine showing a variation-of means for. regulatin: the generating traverse of the c'uttinztool-i Fig. 28 is a vertical section on line 28-2@ of Fig. 27;

Fig. 29 is a horizontal section on line 29-29 of Fig. 28;

Fig. 30 is a section similar to Fig. 28 showing still another variation of means for'controlling the traverse of the cutter;

Fig. 31 is a horizontal section on line 3i3l of Fig. 30.

Like reference characters designate the same parts wherever they occur in all the figures.

Referring first to Figs. 5 and 6, the work is shown at W and the cutter at C. In this instance the work is a series of disks mounted on a flanged arbor i, but may be a single solidgear blank, as will be later explained. The arbor is supported by an adapter 2 held by the upper end of a tubular work spindle 3 which rotates in a bearing sleeve :3 in the machine base 5. The upper end of the arbor is centered, and the work is clamped against the adapter, by an arbor support t having a rotative bearing in an arm I mounted on the base and operated to clamp and release the work in a manner later described.

The cutter is a bar of an alloy steel suitable for metal cutting tools having cutting teeth in a line along one edge. Such teeth are similar to rack teeth in their alinement and outlines at the cutting end, but their sides are tapered inward from the cutting end to avoid rubbing in the cours of their cutting strokes. detachably secured by bolts to a cutter head 8, which in turn is secured to a slide 9 mounted to slide in an undercut guideway ill (see Fig. it) in the forward side of a shiftable holder H which is connected by means of a pivot rod H to a plate l3, which for the purposes of this description may be called the cutter head base, secured to the front wall of the cutter carriage 14.

Where, as in this illustration, the work is mounted with its axis vertical, the cutter is reciprocated up and down in a vertical plane, 1. e., a plane parallel ,to said axis, wherein its path may be either vertical or inclined, -(which path, in either case, is transverse to the length of the cutter bar), and the guideway I is arranged to permitsuch movement. The pivot I2 is perpendicular, or at least transverse, to the direction of the guideway and is provided to permit backing ofl of the cutter from th work on the return strokes. A spring l between a bracket IS on the cutter head base and an abutment H on a rod I8 secured to the slide 9 counterbalances the weight of the slide.

Reciprocating movement is imparted to the cutter head slide by the following means. A motor l9, herein called the cutter driver, drives a crank shaft through a belt and pulley drive 2|, 22, 23. A crank pin 24 on the end of shaft 20 (see also Fig. '7) is coupled to a connecting rod 25 having a screw threaded part engaged adjustably with a rack 26. Said rack meshes with a gear 21. on a rock shaft 28 and fits slidingly in r a guide 29 having pivotal engagement with the rock shaft. Shaft 28 has on its forward end a gear 30 projecting into a recess in the rear side of the slide 9 and meshing with a rack 3| secured to the slide in a line parallel to the guideway III. Hence as the crank pin rotates, the gear to is oscillated and the slide carrying the cutter is reciprocated in the path established by the guideway.

Such path is parallel to the axis of the work piece in cutting spur gears. But it may be in- The cutter is it is connected pivotally to the carriag id to turn about the axis of rock shaft 28, having a sleeve portion 82 which fits a bearing 33 in the carriage and provides a bearing for rock shaft 23. Bolts 35 (Figs. 6 and to) pass through coaxial arcuate slots 35 in the marginal part of the base is into any one of a number of holes 36 in the face of the carriage located at equal distances from the axis of bearing 33, permitting the base and guide to be tilted. The cutter head 8 is likewise adjustable with respect to the slide which carries it, having a centering boss iii. (Fig. 5) which fits a recess in the slide and being secured by bolts 38 entering selected holes in the slide through coaxial arcuate slots in the head. Tilting of the slide enables the cutter to be recip rocated in a path conforming to the helix angle of any helical gear, and the drive through the gear 30 and rack 3! is equally effective regardless of the inclination to which the slide is tilted. The cutter head may-be tilted at an equal and opposite angle'with respect to the slide, whereby to maintain the cutter in a plane perpendicular to the axis of the work, or approximately so, and thus maintain its relationship with the work approximately uniform throughout its generating traverse. When cutting helical gears, a rack type cutter such as that shown at C in Fig. 6a, having teeth at an inclination equal to that of the cutter head slide is substituted for the spur gear cutter C shown in other figures.

Backing'ofi of the cutter and return to the cutting path are efiected by a cam 39 on the crank shaft 20 and coacting springs 65 and 16. The-cam operates a bell crank lever 40 to which is connected a rod 4| projecting toward the holder H and engaging a wear piece 82 therein. The cam through this linkage forces the holder H outwardly until stop shoulders 43 thereon (Fig. 14) engage abutments 44 on the base it. Said stop shoulders are lugs or flanges projecting laterally from the side edges of the holder I I, and the abutments 44 are pieces bolted to the outer face of the base l3 near the lower end of the holder i l, located and formed to overlap the shoulders 43. Spring 45 reacts between base it and the head of a stud secured to the holder, tending constantly to retract the cutter; and

- spring 46 reacts between lever 40 and a stationary part of the carriage structure, causing the lever and transmission rod to recede when permitted by the cam 39.

The cutter carriage I4 is mounted on a slide 41 which is supported on the base 5. The carriage I4 has a rib 48 slidingly fitting a guideway in the slide extending perpendicular to the length dimension of the cutter, and a micrometer screw 48 is mounted rotatably in the slide in mesh with a nut 50 in the carriage for locating the cutter at the correct distance from the axis of the work piece. Any one of various means may be used for indicating and determining the position of the cutter, one such means being illustrated in Fig. 5 as a scale of graduations 5| on the head of the adjusting screw 48 coacting with a stationary index on the base.

Generation of tooth forms in the work by the process according to which this machine operates requires that the cutter be moved lengthwise in a path parallel to the pitch line of its teeth at a rate exactly equal to the linear movement of the cooperating Ditch circle of the simultaneously rotating work piece. To permit of such travel, the slide 41 is supported on tracks 52 and 53 on cllned at any angle, for which purpose the base the h e. h g r: 4 and w i 0 c m! tahicntially oithe work said tracks; and it is guided by a rib- 08, secured to the base parallel to the prescribed path of movement, which is embraced by two pairs of rollers 51 on the slide (Figs. 5,7 and 8). The track 53, which is situated near the cutter, is

Y undercut and a roller 58 on the carriage extends under it to hold the slide and carriage firm against the reaction of the cutter, which cuts during its downward stroke. The carriage I4 is prevented from being lifted away from the slide at such times by clamp bars 59 which are forced by bolts to clamp the flanges 6I of the carriage against the underlying portions of the slide.

Such clamp bars also assist the adjusting screw 40 in maintaining the cutter at the prescribed distance from the work axis. v y The drive for moving slide 41 and rotating work spindle 3 is taken from a motor 62 in the base, which may be called the feed motor. This motor drives, by means of a sprocket 80 and chain 64, a sprocket 65 on shaft 06. Shaft 06 is coupled by clutch elements 81 and 88 (see also 2, 9, 10 and 11) with an alined shaft 80 connected by change gears 10 and II with a shaft 12 which carries a worm l3 meshing with a worm wheel H on the work spindle 3.

A gear IS on shaft '12 meshes with a gear I0 on a short shaft 'l'labove it, which shaft alsocarrles a gear 10 meshing with a gear IS on a screw shaft 80. -The threaded part of the screw shafts fits in a nut 0|. connected with a carriage 82 on which is mounted a bar 03 (Fig. 8) onsingin on abutment 04 on the slide ll. Carriage 82 travels in a path transverse to that of slide 1 4'! and the bar 83 may be set at various angles to the path of its travel, whereby movement of the carriage causes the slide to travel at a rate proportional to the tangent of the angle at which thebarisset.

For convenient definition the bar 83 may be called a wedge or cam bar because it acts as a wedge or cam, and the carriage 82 the wedgebar carriage or slide. This carriage is supported and guided in a fixed path by a track 80 secured to the machine base, and the margins. of the track are engaged On both upper and lower sides by rollers 08 and 01, while its bounding edges are correlation of the pitch line velocities of cutter and work. The transmission mechanism in the base is massive and rigid, and both the wedge carriage and the slide on which the cutter carriage is mounted are accurately guided by nonyielding means. Hence the movements of the cutter between difierent points of its cycle of movements are smooth, even and regular. The

rack type of cutter can be made with finer teeth with an accuracy of spacing, formand dimensions never heretofore obtained. I

Other means than the wedge bar carriage and wedge bar may be employed for imparting generating travel of the cutter. One such alternative means is shown in Figs. 18-21 inclusive. Here a.

, cam 96 having an acting surface of involute curvature is supported to rotate in a horizontal plane above the base in contact with an abutment 91 carried by the slide 47 on a pivot stud 98. The

cam is rotated in harmony with the work spindle by mechanism later described, and transmits linear movement to the carriage 41 proportional to the extent of its angular movement.

The proportional rate of the carriage movement may be altered byturning the abutment about the center of pivot .93 so as to alter the angle of its plane abutment face 39 to the dimetlon of movement of the carriage. Setting of the embraced by rollers 80. all of said rollers being 1 mounted on the carriage. The pivotal connection of the wedge bar with its carriage is made near [one of its ends by a stud". It issecured-at. various angularitiesrby a bolt 00 of which the headoccupies an undercutarcuate slot 0| in the carriage. 82 concentric with the pivot 00. The

abutment Il-is'a block connected-to slide 01 by a! stud 02 (Fig. TL-on which it has a'pivotal mounting. A weight 03. connectedto the slide 41 by a tape or cord 04 passing over a. guide pulley 0! holds the abutment against the wedge bar and causes the carriage to move in one direction when the wedge bar is withdrawn, as well as permits the direction by the abutmentface to a prescribed inclination may be effected by inserting gauge blocks between a pin I00 mounted on a bracketl0l (which forms part of the carriage) and a pin I02 on an extension arm I03 of the block. Adjusting screws I04 and I05 in the bracket I0! and a second bracket I00 respectively serve to shift the abutment and secure it in its different positions of adjustment.

The involute cam and abutment 91 form in effect one tooth of afrack and pinion couple. If.

the abutment face is perpendicular to the path of the slide, the slide is moved at the same linear rate as the base circle of the involute, but when r the abutment is inclined '(by counter-clockwise marriage to move in the other f pressure action of the wedge bar the cutter.

in advancing. 'I'hegcai s''ll'and I0. as well as 10 .and II, are changeable. Substitution for one another ot'gear pairs'having different ratios, connection with wedge bar, V correlated with work gears f all diameters within theme ofthe machine. Due to the wedge different gear pairs.

the mechanism herein dorate of travel 'of the and a very exact tivelr small. number It will be seen that scribed effects a uniform in angular adjustments of the enable the travel of the cutter to be bar. this may be accomplished withfuscof a relarotation with reference to Fig. 20), the cam then moves the slide with thelinear velocity of a pitch circle larger than the .base circle;

In the main, the machine shown in Figs. 19-21 is like that first described, but it has a somewhat different transmission mechanism, with allarger number of changeable gears, for rotating the cam and work spindle. It also exhibits a modification of the means for mounting the cutter head and controlling the relief and return movements of 7 Parts which are substantially identical in the two forms of machine are designated by the same reference characters, while similar parts are designated'by the same characters modifled by exponents.

The cam is secured tea shaft 101 (Fig. 21)

which is driven from a feed motor corresponding to the motor I! by a chain engaging the sprocket "a which, through a train of change gears shown collectively at I00, drives a shaft'tsa coupled by semen 01a with a shaft 12a. The latter-is coupled by a train of change gears shown at I" with a shaft III carrying a-worm III in mesh with a worm wheel l l2 secured to shaft llil. The shaft 120, drives, through a pinion and crown gear couple l l3, a worm ltd meshing with the worm wheel M on the work spindle.

Returning to the cutter of this machine, the cutter head 8 is secured to a plate lla pivoted by means of a pin l2a between lugs Ilt (Fig. 18) on the slide to which has a sliding engagement with the bed, l3 by interlocking undercut guides. The rod ll la for controlling the backing off movement of the cutter is located in the tubular rock shaft 28a and carries an anti-friction roll l l5 engaging an inserted wear piece 321; secured to the plate l Ia by a threaded stud and nut as shown.

A further alternative means for traversing the cutter is shown in Figs. 27, 28 and 29. Here the slide lla supporting the cutter carriage M is propelled directly by a screw 80a which extends in the direction of carriage travel and is driven from the shaft 121) through a gear train llb, lll, lld, M9, l2ll and l2l; the latter gear being secured to the screw, and the gears H8, H9, and l is being mounted on intermediate shafts and being interchangeable with others of different ratios. The

shaft "i212 drives the work spindle through a worm l3 and worm wheel id as first described and is itself driven by essentially similar mechanism to that shown in Figs. l1 for driving the shaft l2.

Screw the engages a nut lZZ on the slide and is movable endwise in its bearing l23 on the base. It is equivalent to a wedge or cam, because, when rotated, its thread acts with wedging eflfect on the carriage, wherefore it may be so called. A bell crank lever having two arms- H4 and l25 is pivoted by a stud I26 to the base. Arm l2l. is forked to embrace the shaft of the screw, and carries pins l2?! projecting between collars l28 on the shaft. The other arm, I25, of the lever carries a pivoted block l29 on its extremity entering. a guideway l3ll in a bar l3l, which likewise is a wedge or cam, and is pivoted by a stud I32 to the slide Ma and is adapted to be swung about its pivot from a position parallel to the screw and the path of movement of the slide to other positions in which it is more or less inclined to such path. It may be set at any prescribed inclination with the aid of gauge blocks, one of which is shown at I32a interposed between pins I33 and :34 mounted respectively on the end of the bar and on an ad-,

. jacent part of the slide; and may be clamped in adjusted position by a screw I35 passing through a slot in the slide into threaded engagement with the bar. As the slide travels, and if the bar I3I is inclined, the bell crank lever moves-the screw endwise more or less, depending on the degree of inclination of the bar I3I, thus giving an increment of movement to the slide additional to that imparted by rotation of the screw. When the guideway in the bar is parallel to the path of the slide, no such incremental movement isimpa'rted. The adjustment of the guide bar, together with substitutions for the changeable gears, enables the traversing movement of the cutter to be exactly correlated with the rotational movement of gear blanks of any diameter within the range of the machine. In other respects the form of the invention just described is like that first described.

The same ultimate effect may likewise be obtained by imparting incremental rotation to the screw 80a. A means for doing this is shown in Figs. 30 and 31, in which the screw is engaged with the slide 41a in the manner previously described, but is withheld from endwise movement by collars I45 and I48 embracing its fixed supporting bearing I323. The shaft F20 which drives the work spindle through worm and wheel gearing as previously described, is coupled with a shaft Hill by changeable gears I58, I49. Shaft lfi'l' carries one member 856 of differential gearing, the other members of which area gear liil on a shaft l'52 in line with shaft Ml, and intermediate gears lbs and H54 in a rotatable carrier use. Shaft E52 is connected with the shaft of screw 86a by changeable ears I56 and lb'l.

Th gear carrier I55 is provided with worm gear teeth lat meshing with a worm liil l which is driven by shaft Me by a gear pair ltd, shaft lfil and a train of changeable gears l62, Hi3, ltd and lfit. By rotating the carrier l55, a speed differential is introduced in the drive from shaft it? to shaft I52, which can be varied by substitutions in the gear train lGZ-I'SE. When any of the gears of this train is removed, the carrier is held stationary by worm I59. The incremental movement which may be thus imparted to the screw supplements the effect of changing the other gears to meet all conditions.

A single machine embodying this invention is capable of producing gears of a wide range of dimensions from pinions 1 s" or less to gears l" or more in diameter, and of a variety of types and thickness or length in the axial dimension. They are cut to finished dimensions with great rapidity, particularly those of the smaller sizes. In order to facilitate changing of the work which, if performed manually, would in many instances require more time than the entire cutting cycle, the machine is provided with a magazine for holding blanks and automatic means for transferring the blanks. to the work spindle, with simultaneous ejection of finished work pieces, and clamping them on the spindle. I willnow describe the embodiment of magazine, work holder and mechanism for operating them in timed relationship disclosed in the drawings.

Figs. 15, 16 and 1'1 show the details of one form of magazine. This is designed to accommodate gear blanks in the form of thin disks which are strung on an arbor I having a base flange ltt and a pin l6! for preventing rotary shifting of the disks with respect to one another. This magazine is made of separable parts I68 and ltd secured together by screws I10 and having an internal space of suitable dimensions to receive the gear blank and arbor assemblages in a row side by side. These parts have ribs on one edge collectively forming a dovetail I'II which flts adjustably, and is clamped, in a groove I12 of a magazine holder I13 by screws I14. An adjusting Lscrew H5 mounted in the holder is provided with a flange entering 'a groove in the rib Hi to aid in exactly locating the magazine with respect to the work spindle.

A pusher I16 is contained slidingly in the slot or guideway I11 provided between the outer lips of the two parts of the magazine and is connected with a spring metal tape I18 like the springs used inwatches and clocks, which extends along the inner wall of the magazine and around a guide roll I19 to a shaft I" to which its other end is secured and around which it is coiled under tension. The effect of the spring is to move the pusher and advance the blanks toward and out of the end of the magazine nearest the work spindle when permitted by withdrawal of blanks. The pusher may be retracted manually toward the outer end of the magazine, having a. projection for en ement by the operators finger for that purpose, to permit loading. A

v cam.

retainer IBI is-connected to the discharge end of the magazine by a pivot I82. It has two separated hooks I83 arranged to embrace the blanks .and engage the extremities of the arbor i or the endmost assemblage. The retainer and its books are so located by an adjustable stop screw I84 and opposing spring 185 acting on a lug i86 which projects from the retainer between the screw and spring, that the outermost blank is clear of the magazine but is held firmly in engagement with the hooks by pressure transmitted through the other blanks from the pusher. The engaging edges of the hooks slightly overlap the blank arbor l at such a small angle to the path of that end of the magazine in moving toward and away from the work spindle that they are displaced by the arbor against the yielding r sistance of spring I85 when the magazine with- (Fig. 11).

iii

draws from the work spindle after the latter has Said magazine holder is mounted on a splined shaft l81,having a divided hub fitting the shaft and being clamped on the same atthe proper height with respect to the worlt spindle by screws I88. Said shaft is suitably located, and the magazine suitably adjusted, to enable the outermost blank to be brought into alinement with the wort: spindle axis (indicated by the letter A in Fig. 15 by partial rotation of the shaft.

An ejector H39 in the spindle (Figs. 5, d and 22) and the arbor support or clamp ii previousl described are operated in time with the movements of the magazine to release a completed work piece and pick off the blank presented by the magazine. The ejector is mounted for endwise movement within the worlr spindle and work adapter .22, and its lower end is engaged by an operating lever ltd. The arm "l which carries the arbor support is. as best shown in Figs. 22 and 23, attached. to a bracket ldi which is ac cured, With provision for adjustment as to height, by a clamp ltll, on an endwise movable bar. or shaft ltd. Shaft 5% passes through a guideway ltd in the base and is engaged with an operating lever ltd. The bracket ldi is also engaged slidingly with a parallel guide bar lit which is fitted tightly in a socket Hill and serves to maintain bracket liila and guide bar illtc diner slightly in form and position, but in all essential respects are like the form of Figs. 18-23 and correspond with the foregoing description.

The operating levers Hit and tell are actuated respectively by cams tilt and llliion a shaft l dl. Said shaft drives by means of a gear couple 2W2 (Fig. 13) a shaft 203 carrying a cam tilt (Fig. 9), which acts on a lever 205 secured to the magazine carrying shaft it'l A spring ltd (Fig. 21 is shown as holding the lever against the It may be understood without specific illustration, that suitable sp ings y be Provided to supplement gravity in lowering the work ejector and arbor support.

The cam shaft 2M is driven by the feed motor.

62 by a sprocket 201 (integral or otherwise connected with sprocket ll) chain Mia and sprocket 2M loose on the shaft 209 (Fig. 11) Two ratchet wheels 2! and 2 are keyed to shaft 209. The ratchet wheel 2! l' is connected with a gear 2I2 in mesh with a gear 2 l3 which is keyed to a shaft 2 (Fig. 9). The latter shaft is in line with the cam shaft but is rotatable independently and is put in driving connection with it at prescribed times by normally disconnected clutch elements H5 and H6. The ratchet 210 is connected with a gear element 2i! which drives shaft 2 I 4 through a gear 2|8 thereon and an intermediate gear 2E9 Bawls 226 and 228 carried by the sprocket 206 coast with the ratchets 210 and 2H respectively. These pawls and ratchets con-.

stitute overrunning or one way clutches of which the clutch all-cit drives the shaft 2% when the sprocket rotates clockwise (with respect to Fig. 12) and the clutch 228-4! drives the shaft when the sprocket rotates counter-clockwise. The feed :motoris reversible and runs in alternately opposite directions to cause gear generation during traverses of the cutter both from left to right and irom right to left. Due to the overrug clutches and the two driving trains, one of which contains one more gear than the other, the shaft tilt is rotated always in the same direction.

The cycle of, the machine comprises traverse oi the cutter in one direction and rotation of the work spindle through an angle sufiicient to out one gear; arrest of the generating movements ill iii

connecting and disconnecting the clutches and lie -2% periormed by a solenoid 222 under control oi the wedge bar carriage The core 22d of the solenoid (Fig. "ll is coupled by a linh 22d with a. lever 222d pivoted at to a bracket in the base.

' a limit ill? with an arrn scorn-ed toe. rock shalt 22b to which also is secured a iorlred arm ill) embracing and coupled to the slidable clutch element till which is spliced to shaft in the normal position or these parts, when the solenoid is inactive, the core of the solenoid is raised and the clutch element bl engagcdwith the complemental clutch element, by a spring. The spring for this nose may be applied to any part of the t and it is shown diagrammatically in Fig. 7 as connected between the top. of the base and lever tilt at the location till.

I fihe clutch. element tit is spliced to shaft tilt and is pressed toward the other clutch elementby a spring 232. It is normally held out of eneasement by a stop 233 having a-wedge surface 334 (Fig. 9). and an arresting shoulder 23b coasting with a pin 2% which projects from the clutch member BIB. The stop .253 is pivoted. to a bracket ZB'lwhichpermits it to move toward and. awayirom the clutch member but holds it rigid against movement parallel to the axis or the clutch. A springitb (Fig. '7) normally holds the stop against the side .of the clutch member in the path of the stop pin 33, and returns it thereto after being displaced. A trip 239 is carried by lever 225 or link 22G (conveniently by the pivot connecting these parts) beside the stop and is Lever is coupled by 

